Compression System for Internal Combustion Engine Including a Rotationally Uncoupled Exhaust Gas Turbine

ABSTRACT

As one example, a vehicle propulsion system is provided. The system includes: an engine with an intake air compressor and an exhaust gas turbine. Further, a control is provided to operate the compressor at a different speed than the turbine, at least under an operating condition, and to adjust an amount of opening overlap between engine valves in response to a rotational speed of the compressor.

BACKGROUND AND SUMMARY

Internal combustion engines can utilize turbochargers or superchargersto obtain increased intake air pressure to enable increased engineperformance. Turbochargers typically include an intake air compressorrotationally coupled with an exhaust gas turbine, where the turbineprovides thrust to the compressor by extracting energy from the exhaustflow. Some of turbochargers may include a motor to assist the compressordevelop sufficient thrust when the turbine is unable to extract enoughenergy from the exhaust flow or where the exhaust flow has insufficientenergy to power the compressor.

The inventors of the present application have recognized that onedisadvantage of the above turbocharger is that the compressor andturbine are rotationally coupled, which can limit the operating state atwhich the compressor and turbine can be operated. For example,compressor surge can be reduced by increasing an amount of exhaust flowbypassing the turbine, which can be achieved by increasing an opening ofa wastegate arranged in a bypass passage of the turbine. By reducing theamount of exhaust energy that is extracted by the turbine, the speed andresulting boost pressure provided by the compressor can be reduced dueto the rotational coupling, thereby reducing or eliminating compressorsurge. However, by increasing the bypass flow of exhaust gases, theefficiency of the engine system may also be reduced since a greateramount of exhaust energy is transferred to ambient by way of thewastegate without being extracted by the turbine.

The inventors have provided various approaches, disclosed herein, thatmay address at least some of the above issues by a vehicle propulsionsystem that comprises: an internal combustion engine including at leastone cylinder; an intake air compressor communicating with the cylindervia an intake valve; an electric machine rotationally coupled to a shaftof the compressor; an exhaust gas turbine communicating with thecylinder via an exhaust valve; and a control system configured tooperate the compressor at a different speed than the turbine, at leastunder an operating condition, and to adjust the electric machineresponsive to conditions of compressor surge to reduce the surge whilecontinuing to extract energy from an exhaust flow of the engine via theexhaust gas turbine. Note that the turbine wastegate may still be usedwith this approach to control turbine operation, however, by adjustingthe electric machine rotationally coupled with the compressor to adjustcompressor speed and/or torque, surge may be reduced or avoided,enabling a reduction in the amount of exhaust flow that is divertedthrough the turbine bypass. In some examples, the wastegate and turbinebypass passage may be entirely eliminated, thereby reducing the cost andcomplexity of the engine system. By reducing the turbine bypass, atleast under some conditions, the turbine can be operated to generateelectrical energy via a second electric machine rotationally coupledwith the turbine, which in turn can be used power the electric machineof the compressor, or other loads.

As another approach described by U.S. Pat. No. 6,647,724, some of thepotential drawbacks of a rotationally coupled compressor and turbine canbe addressed by providing a turbocharger that includes an electriccompressor to boost intake charge pressure supplied to an internalcombustion engine and an electric turbine to generate electrical powerfrom exhaust received from the engine. By operating the electriccompressor mechanically independently of the turbine, turbocharger lagmay be reduced during conditions where a more rapid increase in boostpressure is requested. However, the inventors of the present disclosurehave also recognized that adjustment to the compressor operating stateindependent of the operating state of the turbine can impact the amountof exhaust gas residuals that are retained in the engine cylinders for agiven operating condition. If an insufficient amount or concentration ofresiduals are retained by the engine or if residual retention is toogreat for the given operating conditions, then the efficiency of thesystem may be reduced, misfire may occur, and/or noise, vibration, andharshness (NVH) of the engine may be increased.

The inventors have provided another approach, disclosed herein, thataddresses at least some of the above issues of residual retention, whichincludes as one example, a vehicle propulsion system, comprising: aninternal combustion engine including at least one cylinder; an intakevalve operable to selectively admit at least intake air to the cylinder;an exhaust valve operable to selectively exhaust products of combustionfrom the cylinder; an intake air compressor communicating with thecylinder via the intake valve; an exhaust gas turbine communicating withthe cylinder via the exhaust valve; and a control system configured tooperate the compressor at a different speed than the turbine, at leastunder an operating condition, and to adjust an amount of opening overlapbetween the intake valve and the exhaust valve in response to arotational speed of the compressor. The control system may also adjustthe amount of opening overlap in response to the rotational speed of theturbine or a speed difference between the turbine and compressor. Inthis way, valve timing may be adjusted to retain a prescribed amount ofresiduals in the engine cylinders even when the operating state of thecompressor and turbine are adjusted independently of each other.

The inventors of the present disclosure have recognized further issueswith regards to the previous approaches. For example, some engines mayoperate in one of a plurality of different combustion modes, which caneach utilize different levels of boost as well as different levels ofexhaust gas residual production and retention. If boost is simplyincreased by adjusting the compressor, the amount and/or concentrationof residuals retained by the cylinders may also change, therebypotentially impacting the performance of the engine depending on thecombustion mode presently utilized. For example, two stroke combustionmodes can have higher residual retention rates than four strokecombustion modes, since the valve overlap timings may be shorter in thetwo stroke mode. As another example, spark ignition combustion modes mayutilize a lower concentration of residuals from a previous combustioncycle than a homogeneous charge compression ignition mode whereautoignition is utilized to ignite the fuel and air mixture.

The inventors have provided yet another approach, disclosed herein, thataddresses at least some of the above issues relating to residualretention, which includes as one example, a method of operating anengine, comprising: during a first operating condition, operating theengine in a first combustion mode while adjusting the compressor toprovide a higher level of boost to the engine and operating the turbineat a first speed difference relative to the compressor; and during asecond operating condition, operating the engine in a second combustionmode while adjusting the compressor to provide a lower level of boost tothe engine and operating the turbine at a second speed differencerelative to the compressor. In this way, a suitable level of boost canbe provided to the engine based on the combustion mode presently beingused, while also retaining an amount of exhaust gas residuals in theengine cylinders that is appropriate for the selected combustion mode.

The inventors of the present disclosure have recognized still furtherissues associated with an engine utilizing a rotationally uncoupledcompressor and turbine pair. For example, during warm-up of the engine,if the turbine is operated to extract exhaust gas energy from theexhaust stream, then the exhaust treatment devices may take longer toreach their prescribed operating temperature. However, during theseconditions, additional boost pressure may be requested. Thus, as oneexample, a method of operating a vehicle propulsion system including aninternal combustion engine having an intake air compressor and anexhaust system including an exhaust turbine having a turbine generatorand an exhaust treatment device arranged downstream of the turbine isprovided. The method comprises: during a lower temperature condition ofthe exhaust system, operating the turbine generator to convert a lesseramount of exhaust gas energy produced by the engine to electrical energyand operating the compressor motor at a first speed difference relativeto a speed of the turbine generator; and during a higher temperaturecondition of the exhaust system, operating the turbine generator toconvert a greater amount of exhaust gas energy to electrical energy andoperating the compressor motor at a second speed difference relative toa speed of the turbine generator less than the first speed difference.In this way, the amount of exhaust gas energy removed from the exhaustflow can be adjusted in response to the temperature of the exhausttreatment device to promote rapid heating of the exhaust system, whilealso providing sufficient boost pressure to the engine by way of thecompressor.

The inventors of the present disclosure have recognized still furtherissues. For example, during some operating conditions, a reduced levelof engine boost may be prescribed in order to meet the torque request ofthe vehicle operator, while during other operating conditions, anincreased level of engine boost may be prescribed. The inventors haverecognized that a reduction in engine boost, facilitated by reducingcompressor speed and/or torque, need not necessarily be accompanied by acorresponding reduction in turbine torque or speed when the turbine isrotationally uncoupled from the compressor. For example, during an idlestate of the engine, the turbine may be operated to extract energy fromthe exhaust flow even while the compressor is not operated or when thecompressor is operated to a lesser extent. However, the compressor canserve as an obstruction to the intake system during conditions whereadditional boost is not prescribed for the given engine operating state.Thus, engine efficiency can be reduced during compressor inactivitysince the engine entrains air through the compressor.

As such, the inventors have provided an approach that addresses thisissue, as one example, by a method of operating an internal combustionengine including a first intake air compressor rotationally coupled witha first electric machine and an exhaust turbine rotationally coupledwith a second electric machine, the method comprising: in response to afirst operating state of the engine: increasing a flow of intake airthrough a bypass passage of the compressor relative to a flow of intakeair through the compressor by opening a compressor bypass valve; andgenerating a first amount electrical energy with the second electricmachine by extracting exhaust gas energy flowing from the engine via theturbine; and in response to a second operating state of the engine:decreasing the flow of intake air through the bypass passage of thecompressor relative to the flow of intake air through the compressor byclosing the compressor bypass valve; supplying electrical energy to thefirst electric machine to increase the rotational speed of thecompressor; generating a second amount of electrical energy greater thanthe first amount with the second electric machine by extracting exhaustgas energy from the engine via the turbine; and adjusting the speed ofthe turbine relative to the compressor to vary the second amount ofelectrical energy generated by the second electric machine. In this way,engine efficiency may be increased during conditions where a loweramount of boost is requested or where the compressor is inactive.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a schematic depiction of an example vehicle propulsionsystem.

FIG. 2 shows a schematic depiction of an example cylinder of thepropulsion system of FIG. 1.

FIG. 3 shows a flow chart depicting an example control strategy foradjusting operation of the compressor and turbine in response tooperating conditions.

FIGS. 4A and 4B show flow charts depicting example control strategiesfor coordinating valve timing and overlap with operation of thecompressor and turbine.

FIG. 5 shows a flow chart depicting an example control strategy foradjusting operation of the compressor and turbine in response tocombustion mode of the engine.

FIG. 6 shows a flow chart depicting an example control strategy foradjusting the amount of exhaust residuals that are retained in acylinder of the engine.

FIGS. 7A-7F show graphs depicting example control strategyimplementations.

FIG. 8 shows a flow chart depicting an example control strategy foraddressing compressor surge.

FIG. 9 shows a flow chart for controlling exhaust heating.

DETAILED DESCRIPTION

FIG. 1 shows a schematic depiction of an example vehicle propulsionsystem 100. Propulsion system 100 includes an internal combustion engine110 having a plurality of combustion chambers or cylinders indicated at112, 114, 116, and 118. A more detailed description an example enginecylinder is provided with reference to FIG. 2. While this particularexample shows engine 110 including four cylinders, it should beappreciated that in other examples engine 110 may include any suitablenumber of cylinders.

Engine 110 can receive intake air via an intake system indicatedgenerally at 130 and can exhaust combustion gases via an exhaust systemindicated generally at 150. Intake system 130 can include an air intakepassage 132 that includes a throttle 134. The position of throttle 134can be adjusted by controller 180 to vary the flow rate of intake airprovided to engine 110 as well as the pressure within the intake systemdownstream of the throttle. Intake passage 132 can communicate with acompression device such as compressor 136. A compressor bypass passage138 may be provided to enable intake air to bypass compressor 136. Abypass valve 140 can be arranged along compressor bypass passage 138.The position of bypass valve 140 can be adjusted to vary the proportionof intake air that is directed through compressor 136. In some examples,bypass passage 138 and valve 140 may be omitted.

The outlets of compressor 136 and bypass passage 138 can be combined atan intake passage 142. In some examples, a throttle 141 may be arrangedalong intake passage 142, whereby throttle 134 may be omitted. Thus, athrottle can be arranged upstream and/or downstream of compressor 136.However, in other examples, the intake system may not include athrottle. Intake passage 142 can provide intake air to intake manifold144, which selectively and independently communicates with each ofcylinders 112-118 via their respective intake valves, an example ofwhich is shown in FIG. 2.

An exhaust manifold 152 can be provided to receive products ofcombustion from each of cylinders 112-118. Thus, each of cylinders112-118 can selectively and independently communicate with exhaustmanifold 152 via their respective exhaust valves, an example of which isshown in FIG. 2. Exhaust manifold 152 can provide exhaust gases producedby the various cylinders of the engine to exhaust passage 154. Exhaustpassage 154 can communicate with an exhaust gas turbine 156. A turbinebypass passage 158 may be provided to enable exhaust gases to bypassturbine 156. A bypass valve 160 (e.g. a wastegate) can be arranged alongturbine bypass passage 158. The position of bypass valve 160 can bevaried to adjust the proportion of the exhaust gases that are directedthrough turbine 156. In some examples, bypass passage 158 and valve 160may be omitted. The outlets of turbine 156 and bypass passage 158 can becombined at an exhaust passage 162.

Exhaust passage 162 can include an exhaust treatment device 153. Exhausttreatment device 153 can include one or more exhaust catalysts, traps,filters, or other suitable exhaust treatment components. Exhaust passage162 can also include a sensor 151 for providing a temperature indicationto controller 180 of the exhaust system temperature including thetemperature of exhaust gases flow through exhaust passage 162 and/or thetemperature of exhaust treatment device 153. For example, as shown inFIG. 1, sensor 151 may be coupled directly to device 153. However, inother examples, sensor 151 can be arranged partially within the exhaustflow of exhaust passage 162 upstream or downstream of device 153.

Engine 110 can include an output shaft or crankshaft 120. Crankshaft 120can be coupled to one or more vehicle drive wheels via an intermediatetransmission. In the case where propulsion system 100 is configured as ahybrid propulsion system, crank shaft 120 can also be coupled with agenerator/motor 190, hereafter referred to simply as a motor. Motor 190can include an electric motor as one example. Thus, propulsion system100 can be configured as a hybrid electric vehicle (HEV). Motor 190 canbe selectively operated as a motor or a generator. For example, motor190 can provide work to crank shaft 120 and/or the vehicle drive wheelsduring some conditions and can absorb work from crank shaft 120 and/orthe drive wheels of the vehicle during other conditions, such as duringa regenerative braking operation.

Compressor 136 is shown fixedly coupled to a motor 172 via shaft 137. Asone example, motor 172 can include an electric motor. The speed, torque,and/or direction of rotation of compressor 136 can be adjusted byvarying the amount of electrical power that is provided to or extractedfrom motor 172. Thus, motor 172 can be operated to cause compressor 136to provide boost to the engine or can be operated as a generator,whereby the compressor can remove energy from the intake air flow togenerate electrical energy.

Turbine 156 is shown fixedly coupled to a motor 174 via shaft 157. Asone example, motor 174 can include an electric motor. The speed, torque,and/or direction of rotation of turbine 156 can be adjusted by varyingthe amount of electrical power that is provided to or extracted frommotor 174. As one example, motor 174 can be operated to cause turbine156 to remove energy from the flow of the exhaust gases or can beoperated to add energy to the exhaust gas flow. When the turbine isoperated to remove energy from the exhaust flow, motor 174 can beoperated as a generator. Additionally, the level of exhaust backpressureprovided at the engine can be increased or decreased by varying theoperation of the turbine. For example, exhaust backpressure can beincreased by increasing the amount of energy extracted from the exhaustgas flow by the turbine and exhaust backpressure can be reduced bydecreasing the amount of energy extracted from the exhaust flow.

While operation of motor 174 can be adjusted to vary the backpressureprovided by the turbine, the geometry of the turbine can also beadjusted where it is configured as a variable geometry turbine (VGT). Asone example, the system controller can issue a command signal indicatedat 155 to a variable geometry actuator configured to adjust the turbinegeometry, thereby enable further control over the amount of energyextracted from the exhaust flow and hence the level of exhaustbackpressure attributed to the turbine.

Since compressor 136 is rotationally coupled with motor 172 via shaft137 and turbine 156 can be rotationally coupled with a second motor 174via shaft 157, the compressor and turbine need not rotate about the sameaxis of rotation. Thus, unlike turbochargers having a compressor andturbine that are rotationally coupled with each other, the configurationshown in FIG. 1 enables the compressor and turbine to be packaged withthe engine in alternative configurations. For example, the axes ofrotation of compressor 136 and turbine 156 need not be parallel and canhave various engine system components arranged physically and spatiallybetween them, thereby reducing engine packaging restraints forpropulsion systems that are mounted on a mobile vehicle. However, itshould be appreciated that compressor 136 and turbine 156 can bearranged in some examples so that their axes of rotation are parallel toeach other or are collinear. Furthermore, as shown in FIG. 1, compressor136 can be configured so that it is not rotationally coupled to anyother exhaust turbine of the system and turbine 156 can be configured sothat it is not rotationally coupled to any other compressor of thesystem. Further still, FIG. 1 shows how engine 110 can receive intakeair via only a single compressor and can exhaust products of combustionvia only a single turbine. However, in other examples, two or morecompressors may be arranged in series or parallel along intake system130 having only a single branch or multiple branches; and two or moreturbines may be arranged in series or parallel along exhaust system 150having only a single branch or multiple branches.

Operation of motors 172 and 174 can be controlled by a motor controller176. Motor 172, which can include an electric machine, can receiveelectrical energy from an energy storage device 178 during a motoroperation and can supply electrical energy to energy storage device 178during a generator operation as directed by motor controller 176.Similarly, motor 174, which can include an electric machine, can receiveelectrical energy from energy storage device 178 during a motoroperation and can supply electrical energy to energy storage device 178during a generator operation as directed by motor controller 176.Furthermore, motor 174 can supply electrical energy to motor 172 viamotor controller 176 and likewise motor 172 can supply electrical energyto motor 174. Energy storage device 178 may include one or morebatteries and/or capacitors for storing electrical energy.

The level of boost provided by compressor 136 and the level of exhaustbackpressure provided by the turbine can also be adjusted by varying theposition of bypass valves 140 and 160, respectively. For example, thelevel of boost can be reduced for a given operating state of thecompressor by opening valve 140 to increase the airflow through bypasspassage 138. Similarly, the level of exhaust backpressure can be reducedfor a given operating state of the turbine by opening valve 160 toincrease the exhaust flow through bypass passage 158. In some examples,such at lower engine speed or engine load, controller 180 can increasethe opening of bypass valve 140 to reduce the flow of intake air throughcompressor 136 to thereby reduce the resistance of the intake systemwhen compressor 136 is not being operated. For example, during an idlecondition, the amount electrical energy delivered to motor 172 ofcompressor 136 can be reduced or eliminated and valve 140 can be opened,while during a higher speed or load condition, valve 140 can be closedand electrical energy can be provided to motor 172 to operate compressor136 to provide increased boost pressure to engine 110.

Where motor 190 is included with propulsion system 100, motor controller176 can adjust the amount of electrical energy generated by motor 190and can vary the amount of electrical energy that is provided to energystorage device 178 and/or used by either of motors 172 and 174.Similarly, motor controller 176 can adjust the amount of electricalenergy generated by motors 172 and/or 174 and can vary the amount ofelectrical energy that is provided to energy storage device 178 and/ormotor 190. FIG. 3 provides a schematic depiction of the various energymanagement modes that may be performed by the motor controller.

Motor controller 176 can be controlled by a system controller 180. Thecombination of controllers 176 and 180 comprise a control system asdescribed herein and shown in greater detail in FIG. 2. Note that insome examples controllers 176 and 180 can be combined as a singlecontroller.

Controller 180 can receive an indication of an operator request via auser input device. For example, the position of an accelerator pedal 122as varied by vehicle operator 124 can be identified by pedal positionsensor 126. In this way, the control system can identify a userrequested torque, speed, or load of the engine.

FIG. 2 shows a schematic depiction of an example cylinder of engine 110controlled by a control system 200. For example, FIG. 2 shows cylinder116 of FIG. 1 in greater detail. Note that the other cylinders of theengine can include a similar configuration as cylinder 116. Cylinder 116is defined by cylinder walls 236 and piston 232 movably positionedtherein. Piston 232 is shown coupled to crankshaft 120. Intake airand/or fuel can be admitted to cylinder 116 from intake manifold 144 viaintake valve 252 and products of combustion can be exhausted fromcylinder 116 via exhaust valve 254. Note that in some examples, eachcylinder of engine 110 including cylinder 116 can include two or moreintake valves and/or two or more exhaust valves.

Intake valve 252 can be controlled by valve actuator 251. In thisparticular example, valve actuator 251 is configured as a cam actuator,whereby valve timing can be adjusted by way varying the position of thecam and/or cam shaft relative to the position of the crankshaft and/orby utilizing cam profile switching whereby a second cam is selectivelyused to provide alternative valve timing. However, in other examples, anelectromagnetic valve actuator may be used instead of a cam actuator.Regardless of the particular intake valve hardware, the opening andclosing timing of the intake valve can be adjusted by system controller180. Sensor 255 can provide an indication of intake valve position tocontroller 180.

Exhaust valve 254 can be controlled by valve actuator 253. In thisparticular example, valve actuator 253 is configured as a cam actuator.However, in other examples, an electromagnetic valve actuator may beused instead of a cam actuator. Regardless of the particular intakevalve hardware, the opening and closing timing of the exhaust valve canbe adjusted by control system 200. Sensor 257 can provide an indicationof intake valve position to control system 200. Exhaust gases can beexhausted from cylinder 116 to exhaust manifold 152 via exhaust valve254.

Fuel can be provided to cylinder 116 via a fuel injector 266. In thisparticular example, fuel injector 266 is configured as a port injector.However, in other examples, fuel injector 266 may be configured as anin-cylinder injector to provide what may be referred to as directinjection. Fuel injector 266 can receive an injection command signalfrom driver 268 in response to a prescribed fuel injection timingprovided by control system 200. Fuel injector 266 can receive fuel froma fuel system (not shown) including a fuel tank, a fuel rail, and a fuelpump.

An ignition device such as spark plug 292 may be configured to providean ignition spark to the cylinder as direct by ignition system 288.Control system 200 can adjust the ignition timing provided by way ofignition system 288.

Control system 200 is provided as a representation of controllers 176and 180 previously described with reference to FIG. 1. Therefore, itshould be appreciated that control system 200 can include a singlecontroller or multiple distinct controllers. Regardless of theparticular configuration, control system 200 can include an input/outputinterface 202 for communicating with various sensors and actuators ofthe propulsion system, a central processing unit (CPU) 204, read-onlymemory (ROM) 206, random access memory (RAM) 208 and/or keep-alivememory (KAM) 210, each of which can communicate via a data bus. Centralprocessing unit 204 can execute instructions stored in memory to carryout the various control methods and routines described herein. Inaddition to the previously described sensors and actuators, controlsystem 200 can receive an indication of the temperature of the engine atcoolant sleeve 214 via sensor 212 and can receive an indication ofcrankshaft position and/or engine speed via a profile ignition pickupsignal (PIP) from Hall effect sensor 218 or other suitable sensorcommunicating with crankshaft 120.

While not shown in FIGS. 1 and 2, intake system 130 and exhaust system150 can include various temperature and/or pressure indicating sensorsthat are arranged in communication with the control system. For example,intake system 130 may include temperature and/or pressure indicatingsensors arranged along intake passage 132 upstream of the compressor aswell as temperature and/or pressure indicating sensors arranged alongintake passage 142 or within intake manifold 144 located downstream ofthe compressor. Exhaust system 150 may include temperature and/orpressure indicating sensors arranged upstream of turbine 156 withinexhaust manifold 152 or exhaust passage 154 as well as temperatureand/or pressure indicating sensors arranged along exhaust passage 162located downstream of turbine 156. These indications of temperatureand/or pressure within the intake and exhaust systems can be used by thecontrol system to identify the level of boost provided by the compressorand the level of exhaust backpressure created by the turbine, as well asenabling the control system to infer the speed, torque, and direction ofrotation of the compressor and turbine, for purposes of feedbackcontrol.

FIG. 3 shows a flow chart depicting an example control strategy foradjusting the operation of the compressor and turbine in response tooperating conditions of the vehicle propulsion system. At 310, operatingconditions of the propulsion system can be identified. For example, thecontrol system can obtain operating condition information from thevarious sensors previously described as well as other suitable sensorsfor providing an indication of the various operating conditionsdescribed below. Operating conditions may include one or more of thefollowing: engine speed, engine torque, engine load, the combustion modeperformed by the engine cylinders, ambient conditions including ambientair temperature and pressure, intake manifold pressure (e.g. boostpressure), exhaust manifold pressure (e.g. exhaust backpressure),exhaust gas temperature, engine temperature, throttle position, intakeand exhaust valve timings and opening overlap, compressor bypass valveposition, turbine bypass valve position, intake and exhaust air flowrates, accelerator pedal position, operating state of the compressor andassociated motor including an indication of the speed, torque anddirection of rotation, operating state of the turbine and associatedmotor including an indication of speed, torque and direction ofrotation, the geometry of the turbine where it is configured as avariable geometry turbine, the operating states of motor 190 and a stateof charge of energy storage device 178, among other suitable conditions.

At 320, a target torque, speed, and/or direction of rotation can beselected for the compressor based on the operating conditions identifiedat 310. At 330, a target torque, speed, and/or direction of rotation canbe selected for the turbine based on the operating conditions identifiedat 310. For example, the control system can reference a map, look-uptable or function stored in memory in response to the identifiedoperating conditions to select the target torque, speed, and/ordirection of rotation for the compressor and turbine. Note that theoperating parameters of the compressor and turbine can be selected inresponse to the same or different operating conditions.

As one non-limiting example, the speed and torque at which thecompressor is operated can be coordinated with the speed and torque atwhich the turbine is operated to control the amount of residuals thatare retained in the engine cylinders. For example, as the amount ofenergy extracted from the exhaust flow by the turbine is increased (e.g.by increasing negative torque and speed of the turbine), the exhaustbackpressure provided by the turbine may be increased. By increasing theexhaust backpressure, the amount of residuals retained in the cylinderfrom the previous combustion event may be increased, for a given valveoverlap, as shown in FIG. 7A for example. By instead reducing the amountof exhaust flow energy that is extracted by the turbine (e.g. byreducing negative torque or providing positive torque to the exhaustflow), the exhaust backpressure may be reduced, thereby reducing theamount of residuals retained by the cylinder for the given valveoverlap.

As another example, as the level of boost provided by the compressor isincreased (e.g. by increasing positive compressor torque and/or speed)for a given valve overlap, the amount of residuals retained in thecylinder may be reduced, as shown in FIG. 7B for example. Conversely,the amount of residuals retained in the cylinder may be increased forthe given valve overlap by reducing the level of boost provided by thecompressor (e.g. by reducing the positive torque and/or speed of thecompressor).

Further still, the valve overlap can be adjusted for a given set ofcompressor and turbine operating parameters as shown in FIG. 7C. Forexample, the amount of residuals retained by the cylinder may beincreased by reducing valve overlap and/or by adjusting the relativetiming of exhaust valve opening and closing relative to piston position.Conversely, the amount of residuals retained by the cylinder may bereduced by increasing the valve overlap and/or by adjust the relativetiming of the exhaust valve opening and closing relative to pistonposition.

Since the compressor and turbine are not mechanically coupled with eachother and are instead able to be driven independently of each other viatheir respective motors, the retention of residuals within the enginecylinders can be more effectively controlled. For example, thecompressor speed and torque can be adjusted relative to the turbinespeed, torque and direction of rotation, thereby enabling a controlresponse where only one of the devices responds to a requested increaseor decrease in the amount of residuals retained by the cylinder; or thecontrol system can respond to a request for more or less residualretention by adjusting the compressor and turbine at different rates,consonant with their respective response time and hardware limitations.

At 340, operation of the compressor motor can be adjusted to achieve thetarget torque, speed, and/or direction of rotation that was selected at320. Similarly, at 350, operation of the turbine can be adjusted toachieve the target torque, speed, and/or direction of rotation that wasselected at 330. Next, the routine may return where feedback orfeedforward control may be used to control the turbine and compressoroperations in response to changing operating conditions.

FIG. 4A is a flow chart depicting an example of how the valve timings orvalve overlap may be adjusted in response to compressor and/or turbineoperations. At 410 and 412, the torque, speed, and/or direction ofrotation can identified for the compressor and the turbine,respectively. For example, the control system can obtain an indicationof compressor speed, torque, and/or direction of rotation from motor 172and an indication of turbine speed, torque, and/or direction of rotationfrom motor 174. In other examples, shafts 137 and 157 may include speedor torque sensors for providing an indication of compressor and turbinespeeds and torques to the control system. In still other examples, thespeed, torque, and/or direction of rotation of the compressor and/orturbine may be inferred from airflow sensors arranged within the intakeor exhaust systems.

At 414, a torque or speed difference between the compressor and turbinemay be identified at 414. For example, the control system can comparethe indication of compressor speed or torque to the speed and torque ofthe turbine. At 416, the valve timings and/or valve opening overlap canbe adjusted in response to the difference between the torque and/orspeed of the compressor and turbine as identified at 414. Additionallyor alternatively, the opening overlap can be adjusted in response to arotational speed of the engine. For example, the opening overlap of theintake and exhaust valves can be increased with increasing engine speedfor a given compressor operating state.

As one non-limiting example, the control system can increase the amountof overlap between the exhaust valve closing timing and the intake valveopening timing with decreasing compressor torque and/or speed; or theamount of overlap may be reduced as the compressor torque and/or speedare increased. This approach may be used, for example, to maintain aprescribed level of residuals within the engine cylinders whileadjusting the level of boost that is provided to the engine by thecompressor. However, in other examples, the amount of overlap betweenthe intake and exhaust valve timing may be increased with increasingboost provided by the compressor or may be reduced with decreasingboost. As described with reference to FIGS. 5 and 6, the amount ofresiduals that are retained in the cylinder can be varied with respectto the type of combustion mode carried out by the cylinder.

FIG. 4B is a flow chart depicting an example of how the compressorand/or turbine may be instead adjusted in response to valve timingand/or valve overlap. At 430, the opening and closing timing of theintake valves can be identified. For example, the control system canidentify the position and hence the timing of the intake valve openingand closing from sensor 255. At 432, the opening and closing timing ofthe exhaust valve can be identified. For example, the control system canidentify the position and hence the timing of the exhaust valve openingand closing from sensor 257.

At 434, the valve overlap between the closing of the exhaust valve andthe opening of the intake valve can be identified, for example, bycomparing the valve timings identified at 430 and 432. At 436, therelative speeds and/or torques of the compressor and turbine can beadjusted in response to the valve overlap identified at 434. Forexample, the control system can increase or decrease the speed and/ortorque of the compressor relative to the turbine; or the control systemcan increase or decrease the speed and/or torque of the turbine relativeto the compressor. Note that the speed and torque of the turbine orcompressor can be controlled independently such that the speed may beincreased while the torque is reduced and/or vice versa.

In this way, the operation of the turbine and/or compressor can beadjusted in response to valve timing or valve overlap. Thus, where aprescribed level of combustion residuals are to be retained within thecylinder, the valve timing and boost can be coordinated. For example,the control system can increase the relative speed and/or torquedifference between the compressor and turbine with increasing ordecreasing valve overlap to retain the prescribed amount of residualswithin the cylinder. As described with reference to FIGS. 5 and 6, thelevel of residuals to be retained by the cylinder can be dictated by thecombustion mode of the cylinder.

FIG. 5 is a flow chart depicting an example control strategy foradjusting compressor and/or turbine operation in response to thecombustion mode of the cylinder. At 510, the operating conditions of thepropulsion system can be identified. The operating conditions identifiedat 510 can be the same as those previously described at 310. Forexample, the control system can identify current and/or target enginespeed, engine torque, and/or engine load conditions.

At 512, in response to the operating conditions identified at 512, acombustion mode can be selected. Note that combustion mode can beselected on an individual cylinder basis or can be selected for theengine as a whole. As one example, the control system can reference acombustion mode map or look-up table stored in memory for the givenoperating conditions to enable selection of at least one combustion modeto be carried out by the cylinder. For example, at higher engine loadsor engine speeds, a first combustion mode may be selected, whereas atlower engine loads or engine speeds, a second combustion mode may beselected.

In this particular example, one of several combustion modes may beselected by the control system as judged at 514, 516, 518, and 520.However, in other examples, a fewer number or greater number ofcombustion modes may be available for selection. Further still, in someexamples, the combustion mode or number of available combustion mode maybe selectable the vehicle operator via a user selectable combustion modeswitch.

If, at 514, a four stroke compression ignition (CI) mode is to beperformed by the cylinder, then the routine can proceed to 522, wherebythe compressor and/or turbine operation can be adjusted for the fourstroke compression ignition mode and compression ignition of an air andfuel charge can be performed by the cylinder once every 720 crank angledegrees.

As one non-limiting example, the CI mode, whether four stroke or twostroke, may include what may be referred to as homogeneous chargecompression ignition (HCCI), whereby the air and fuel charge isauto-ignited by compression performed by the piston. In contrast todiesel type compression ignition where an injection of fuel is utilizedto initiate combustion, auto-ignition of the charge by HCCI can beinduced by adjusting the temperature and pressure within the cylinder toa level sufficient for self ignition at the prescribed ignition timing.Additionally, the fuel used during HCCI can include gasoline as opposedto diesel fuel. One approach for controlling the temperature andpressure within the cylinder and hence the auto-ignition timing is tovary the amount of residuals retained by the cylinder from the previouscombustion cycle. During the CI mode and more particularly by way ofHCCI, the speed and/or torque of the compressor (or turbine) can beadjusted to target speed and torque setpoints for a given set ofoperating conditions. In this way, a target or prescribed amount ofresiduals can be retained in the cylinder for facilitating the fourstroke CI mode.

If, at 516, a two stroke compression ignition mode is to be performed bythe cylinder, then the routine can proceed to 524, whereby thecompressor and/or turbine operation can be adjusted for the two strokecompression ignition mode and compression ignition of an air and fuelcharge can be performed by the cylinder once every 360 crank angledegrees. As one example, the compressor may be operated to provideincreased levels of boost during the two stroke mode in order to respondto increased residual retention that may occur during the two strokemode relative to the four stroke mode, since valve overlap events can beshorter during the two stroke operation. In this way, a target orprescribed amount of residuals can be retained in the cylinder even whenthe cylinder can operate in a four stroke mode during some conditionsand a two stroke mode during other conditions.

If, at 518, a four stroke spark ignition (SI) mode is to be performed bythe cylinder, then the routine can proceed to 526, whereby thecompressor and/or turbine operation can be adjusted for the four strokespark ignition mode, where the air and fuel charge can be ignited withinthe cylinder by the spark plug at a frequency of once every 720 crankangle degrees. Note that the target amount of residuals to be retainedby cylinder may be less during the SI modes than the CI modes, sinceignition of the air and fuel charge is initiated by an ignition sparkrather than by compression performed by the cylinder.

If, at 520, a two stroke spark ignition mode is to be performed by thecylinder, then the routine can proceed to 528, whereby the compressorand/or turbine operation can be adjusted for the two stroke compressionignition mode and compression ignition of an air and fuel charge can beperformed by the cylinder once every 360 crank angle degrees. In someexamples, the level of boost provided by the compressor can be greaterduring two stroke SI than during four stroke SI in order to reduce thelevel of residuals retained by the cylinder, which may be due to theshorter valve overlap in the two stroke mode.

At 530, the valve timings and/or valve overlap of the cylinder can beadjusted in response to the selected combustion mode and can be adjustedin response to the compressor and/or turbine adjustment performed at oneof operations 522, 524, 526, and 528 as previously described withreference to operation 416 of FIG. 4A. Thus, adjustment of the valvetimings and overlap can be coordinated with turbine and compressoroperations to retain a residual amount appropriate for the selectedcombustion mode.

While various combustion modes have been described with reference toFIG. 5, including a homogeneous charge compression ignition mode, aspark ignition mode, two stroke mode, and a four stroke mode, stillother combustion modes may be carried out by the engine cylinders. Forexample, some spark ignition modes may carry out combustion during afirst condition by igniting a stratified charge and during anothercondition by igniting a homogeneous charge. Similarly, compressionignition modes may utilize ignition of a homogeneous charge during afirst condition and stratified charge ignition during a secondcondition. Where a stratified charge is to be generated within thecylinder, a first earlier fuel injection can be performed by theinjector to create a more homogeneous mixture in the combustion chamberfollowed by a second later fuel injection that creates a rich region offuel in the vicinity of the ignition source, such as a spark plug, forexample.

Regardless of the various combustion modes employed by the engine, thecompressor and turbine can be operated at independently selectable speedand torque setpoints for a given set of operating conditions. Forexample, during a first combustion mode, the turbine and compressor canbe operated with a first speed and/or torque difference for a given setof operating conditions. During a second combustion mode, the turbineand compressor can be operated with a second speed and/or torquedifference for the given set of operating conditions. In this way, alevel of boost that is suitable for each combustion mode can be providedby the compressor, while the turbine can be operated to vary theretention of residuals suitable for the particular combustion mode ofthe engine cylinders.

As a non-limiting example scenario, the control system can operate theengine so that during a first operating condition, the engine isoperated in a first combustion mode while adjusting the compressor toprovide a higher level of boost to the engine and turbine is operated ata first speed difference relative to the compressor; and during a secondoperating condition, engine is operated in a second combustion modewhile adjusting the compressor to provide a lower level of boost to theengine and the turbine is operated at a second speed difference relativeto the compressor. The first operating condition can include a differentengine speed or engine load than the second operating condition, forexample. In this way, a boost pressure suitable for a given combustionmode of the engine may be provided while also retaining a level ofexhaust gas residuals within the engine cylinders by controlling therelative speeds of the compressor and turbine.

FIG. 6 shows a flow chart depicting an example control strategy foradjusting the amount of exhaust residuals that are retained in acylinder of the engine. At 610, the control system can identifyoperating conditions of the vehicle propulsion system, for example, aspreviously described with reference to 310. For example, the controlsystem may identify the present combustion mode of the cylinder or aprescribed combustion mode to which the cylinder is to be transitioned,among other operating conditions.

If at 612, the amount of residuals to be retained by the cylinder is tobe increased, then one or more of the operations at 616-622 may beperformed. Alternatively, if residual retention is not to be increased,then the routine may proceed to 614. For example, the control system mayjudge whether to increase or decrease residual retention based on thecurrent operating conditions including the present combustion mode aswell as operator input indicative of user requested torque. Where achange in operating conditions dictates a transition to a differentcombustion mode, the control system may judge at 612 that the amount ofresiduals retained by the cylinder is to be increased or alternativelyreduced as will be described with reference to 614. Note that thecontrol system can reference a look-up table, mode map, or otheralgorithm stored in memory to identify an appropriate amount ofresiduals to be retained based on operating conditions including engineload, engine speed, and engine torque requested by the operator for thegiven combustion mode.

In order to increase residual retention, the compressor operation may beadjusted to reduce the level of boost provided to the cylinder by thecompressor. As one example, the control system may reduce the amount ofelectrical energy (e.g. electrical power) provided to the compressormotor to reduce compressor speed and/or torque, thereby reducingcompressor boost. As another example, the compressor bypass valve may beopened to reduce the flow of intake air through the compressor, therebyreducing boost and increasing residual retention.

At 618, operation of the turbine may be adjusted to increase exhaustbackpressure, thereby enabling an increase in the amount of residualsretained by the cylinder. For example, the control system can increasethe amount of electrical energy that is produced by the turbine motorfrom the conversion of the kinetic and thermal energy of the exhaustflow into electrical energy, thereby increasing exhaust backpressure atthe cylinder. As another example, the exhaust flow through the turbinebypass (if any) may be reduced by closing the turbine bypass valve. Inthis way, exhaust backpressure may be increased, thereby increasingresidual retention.

At 620, the valve timing may be adjusted to reduce the valve overlapbetween the opening of the intake valves and the opening of the exhaustvalves. By reducing the valve overlap, the amount of residuals retainedin the cylinder may be increased. At 622, the throttle position can becoordinated with the various adjustments performed at one or more ofoperations 616, 618, and 620, to maintain the prescribed airflow to theengine. For example, where compressor boost is reduced, the throttle canbe opened to a greater extent to maintain a target airflow rate to thecylinder. In this way, fluctuations in torque that may be caused byadjustment to the residual retention rate at the engine may be reduced,particularly where a reduction in compressor boost is performed toenable an increase in residual retention levels.

If it is instead judged at 614 to reduce the residual retention, thenone or more of operations 624-630 may be performed. For example, at 624,the operation of the compressor may be adjusted to increase the level ofboost provided to the engine. The control system may increase the amountof electrical energy that is provided to the compressor motor toincrease the speed and/or torque of the compressor. By increasingcompressor boost, the amount of residuals retained in the cylinder maybe reduced, particularly where valve overlap is utilized.

At 626, the operation of the turbine may be adjusted to reduce exhaustbackpressure at the engine. For example, the control system can extractless energy from the exhaust flow via the turbine, which can beconverted to electrical energy by the turbine motor; or the turbine canprovide energy to the exhaust flow. By reducing the extraction rate ofenergy from the exhaust flow or by providing energy to the exhaust flow,the backpressure at the engine may be reduced, thereby reducing residualretention at the cylinder.

At 628, the valve timing may be adjusted to increase valve overlap. Theincrease in valve overlap can increase the exchange of fresh intake airto the cylinder and can increase removal of exhaust gas residuals fromthe cylinder. Additionally, the throttle position can be adjusted incoordination with an adjustment made at one or more of operations 624,626, and 628, to maintain a prescribed airflow to the engine. Forexample, the throttle can be further closed in response to an increasein boost provided by the compressor to reduce the additional mitigatethe effects of the added airflow that would be provided to the engine.In this way, fluctuations in torque that may be caused by adjustment tothe residual retention rate at the engine may be reduced, particularlywhere increased compressor boost is used to reduce residual levels.

FIGS. 7A-7F show graphs depicting example control strategyimplementations. FIG. 7A shows an example depicting how the amount ofresiduals retained in a cylinder of the engine can be increased byadjusting operation of turbine to increase exhaust backpressure, whilevalve overlap and compressor boost can remain substantially unchanged.Conversely, the amount of residuals may be reduced by reducing theexhaust backpressure imparted by the turbine. The exhaust backpressurecreated by the turbine can be increased, for example, by extractingadditional energy from the exhaust gas flow.

FIG. 7B shows an example depicting how the amount of residuals retainedin the cylinder of the engine can be increased by adjusting operation ofcompressor to reduce the level of boost provided to the engine, whilevalve overlap and compressor boost can remain substantially unchanged.Conversely, the amount of residuals retained in the cylinder can bereduced by adjusting operation of compressor to increase the level ofboost provided to the engine.

FIG. 7C shows an example depicting how the amount of residuals retainedin the cylinder of the engine can be increased by reducing a valveoverlap between an opened state of the intake and exhaust valves, whileturbine and compressor operations can remain substantially unchanged.Conversely, the amount of residuals retained in the cylinder can bereduced by increasing the valve overlap.

FIG. 7D shows an example depicting how the amount of residuals retainedin the cylinder may be adjusted by varying two or more operatingparameters including the turbine and/or compressor operations, as wellas the valve overlap as previously described with reference to FIGS.7A-7C.

FIG. 7E shows an example depicting how the amount of residuals retainedin the cylinder may be adjusted by first adjusting a first operatingparameter and subsequently adjusting a second operating parameter. Forexample, FIG. 7E shows how compressor boost may be first reduced andturbine created backpressure may be subsequently increased to increaseresidual retention. Thus, different operating parameters such asturbocharger operation, compressor operation, and/or valve operation maybe adjusted in a different order or concurrently depending on whetherthe residual retention is to be increased or decreased.

FIG. 7F shows an example depicting how the amount of residuals retainedin the cylinder may be adjusted by varying two operating parameters atdifferent rates. For example, FIG. 7F shows how the turbine operationmay be adjusted to reduce backpressure to a lesser extent than areduction in compressor boost, thereby causing an overall increase inthe amount of residuals retained. Thus, one or more operating parameterscan be adjusted in a direction that increases residual retention whileone or more other operating parameters can be adjusted in a directionthat reduces residual retention, whereby the overall change in theamount of residuals retained by the cylinder can be based on therelative rate of change of the these operating parameters.

FIG. 8 shows a flow chart depicting an example control strategy foraddressing compressor surge. At 810, the control system can identifyoperating conditions relevant to compressor surge. Of the variousoperating conditions described with reference to operation 310, thecontrol system may utilize an indication of compressor speed and torquefor a given volumetric flow rate of intake air through the compressor aswell as the pressure ratio across the compressor. For example, thecontrol system can reference a compressor surge map stored in memory toenable the control system to selectively operate the compressor withinsuitable ranges of operating conditions where compressor surge does notoccur.

However, during some conditions, such as at lower engine speeds and/orlower volumetric intake airflow conditions, sufficiently high compressorspeed may result in compressor surge. Compressor surge can be reduced byreducing compressor speed relative to the volumetric flow rate of intakeair through the compressor. Therefore, at 812, it may be judged whetherto reduce compressor speed. If the answer at 812 is yes, the routine mayproceed to 814. If the answer at 812 is no, the routine may return.

At 814, the amount of electrical energy or power provided to thecompressor motor can be reduced to reduce the compressor speed. Incoordination with the reduction of compressor speed, the throttleopening can be increased to maintain the prescribed airflow to theengine as indicated at 816. The compressor bypass valve opening can alsobe increased to further reduce compressor surge.

FIG. 9 shows a flow chart depicting an example approach for controllingcompressor and turbine operation during different exhaust systemtemperature conditions. At 910, the temperature of the exhaust systemincluding the temperature of an exhaust treatment device can beidentified. At 912, if the temperature of the exhaust system and/orexhaust treatment device is greater than a threshold temperature, theroutine can proceed to 916, where an increased conversion of exhaust gasenergy to electrical energy can be performed by the turbine andassociated motor. Alternatively, if at 912, the temperature of theexhaust system and/or exhaust treatment device is not greater than thethreshold temperature, then the routine can proceed to 914 where areduced conversion of exhaust gas energy to electrical energy can beused. For example, depending on the temperature condition of the exhaustsystem, the control system can adjust the geometry of the turbine, theflow rate of exhaust gas bypassing the turbine (e.g. via valve 160),and/or the torque load of motor 174 to vary the backpressure provide bythe turbine as well as adjusting the amount of exhaust gas energy thatis extracted from the exhaust flow. In this way, during a cooler exhausttemperature condition, such as during start-up of the engine or during awarm-up phase of the exhaust system, increased exhaust energy can beprovided to the exhaust treatment device to promote more rapid heating.When sufficient heating of the exhaust treatment device has occurred,for example, when the temperature exceeds the threshold, the amount ofexhaust energy extracted by the turbine may be increased, whereby theturbine motor can generate additional electrical energy.

At 918, the compressor can be operated to provide a suitable boostpressure and cylinder scavenging of exhaust residuals (e.g. responsiveto valve overlap) for the selected combustion mode. For example, thecompressor can be operated at different speed differences than theturbine during warmer and cooler conditions of the exhaust system inorder to maintain an appropriate boost pressure at the engine and retaina prescribed level of residuals even when the turbine speed varies withexhaust system temperature.

As another non-limiting example scenario utilizing some of thepreviously described approaches, a vehicle propulsion system maycomprise an internal combustion engine including at least one cylinder;an intake valve operable to selectively admit at least intake air to thecylinder; an exhaust valve operable to selectively exhaust products ofcombustion from the cylinder; an intake air compressor communicatingwith the cylinder via the intake valve; a first electric machinerotationally coupled with the compressor; an exhaust gas turbinecommunicating with the cylinder via the exhaust valve; a second electricmachine rotationally coupled with the compressor; and a control systemhaving memory containing executable instructions to: during an earlystage of an acceleration event of the vehicle, provide an initial higherboost pressure to the engine via the compressor by adjusting a speed ofthe first electric machine relative to a speed of the second electricmachine, and operate the intake and exhaust valves to provide aninitially smaller amount of opening overlap between the intake valve andthe exhaust valve; and during a later stage of the acceleration event ofthe vehicle, provide a subsequently lower boost pressure to the enginevia the compressor by adjusting the speed of the first electric machinerelative to the speed of the second electric machine, and operate theintake and exhaust valves to provide a subsequently larger amount ofopening overlap between the intake valve and the exhaust valve. In thisway, the control system can adjust the boost pressure provided to theengine during an acceleration event in order to meet the engineperformance request of the vehicle operator, while also adjusting thevalve overlap in response to the boost provided by the compressor tomaintain a suitable level of exhaust gas residuals in the enginecylinders.

Note that the example control and estimation routines included hereincan be used with various engine and/or vehicle system configurations.The specific routines described herein may represent one or more of anynumber of processing strategies such as event-driven, interrupt-driven,multi-tasking, multi-threading, and the like. As such, various acts,operations, or functions illustrated may be performed in the sequenceillustrated, in parallel, or in some cases omitted. Likewise, the orderof processing is not necessarily required to achieve the features andadvantages of the example embodiments described herein, but is providedfor ease of illustration and description. One or more of the illustratedacts or functions may be repeatedly performed depending on theparticular strategy being used. Further, the described acts maygraphically represent code to be programmed into the computer readablestorage medium in the engine control system.

It will be appreciated that the configurations and routines disclosedherein are exemplary in nature, and that these specific embodiments arenot to be considered in a limiting sense, because numerous variationsare possible. For example, the above technology can be applied to V-6,I-4, I-6, V-12, opposed 4, and other engine types. The subject matter ofthe present disclosure includes all novel and nonobvious combinationsand subcombinations of the various systems and configurations, and otherfeatures, functions, and/or properties disclosed herein.

The following claims particularly point out certain combinations andsubcombinations regarded as novel and nonobvious. These claims may referto “an” element or “a first” element or the equivalent thereof. Suchclaims should be understood to include incorporation of one or more suchelements, neither requiring nor excluding two or more such elements.Other combinations and subcombinations of the disclosed features,functions, elements, and/or properties may be claimed through amendmentof the present claims or through presentation of new claims in this or arelated application. Such claims, whether broader, narrower, equal, ordifferent in scope to the original claims, also are regarded as includedwithin the subject matter of the present disclosure.

1-25. (canceled)
 26. A vehicle propulsion system, comprising: aninternal combustion engine including at least one cylinder with anintake valve and an exhaust; an intake air compressor communicating withthe cylinder via an intake valve; an electric machine rotationallycoupled to a shaft of the compressor; an exhaust gas turbinecommunicating with the cylinder via an exhaust valve; and a controlsystem configured to operate the compressor at a different speed thanthe turbine, at least under an operating condition, to adjust theelectric machine responsive to conditions of compressor surge to reducethe surge while continuing to extract energy from an exhaust flow of theengine via the exhaust gas turbine, and to adjust an amount of openingoverlap between the intake valve and the exhaust valve in response tothe speed difference between the compressor and the turbine.
 27. Thesystem of claim 26, wherein the control system is configured to adjustthe electric machine responsive to conditions of compressor surge byadjusting a rotational speed of the electric machine in response to aflow rate of intake air consumed by the engine.
 28. The system of claim26, wherein the control system is configured to adjust the electricmachine responsive to conditions of compressor surge by adjusting anamount of torque transmitted to the compressor by the electric machinein response to a flow rate of intake air consumed by the engine.
 29. Thesystem of claim 26, wherein the control system is configured to reducean amount of electrical energy supplied to the electric machine toreduce the surge.
 30. The system of claim 26, further comprising asecond electric machine rotationally coupled to a shaft of the turbine;wherein the second electric machine is configured to generate electricalenergy from said extraction of exhaust flow energy by the turbine. 31.The system of claim 30, wherein the control system is further configuredto supply at least a portion of the electrical energy generated by thesecond electric machine to the electric machine rotationally coupled tothe shaft of the compressor.
 32. The system of claim 30 furthercomprising an energy storage device, wherein the control system isfurther configured to supply at least a portion of the electrical energygenerated by the second electric machine to the energy storage device.33. The system of claim 26, wherein the compressor and the turbine donot rotate about the same axis of rotation.
 34. The system of claim 26,wherein an axis of rotation of the compressor is not parallel to an axisof rotation of the turbine.
 35. The system of claim 26, wherein theturbine is not rotationally coupled with any intake air compressor ofthe vehicle propulsion system.
 36. A method for an engine cylinder withan intake and exhaust valve, comprising: operating anelectrically-driven intake compressor at a different speed than anexhaust-driven turbine; adjusting boost by adjusting the compressor toreduce surge while continuing turbine operation; and while adjusting theboost, adjusting an amount of opening overlap between the intake andexhaust valves in response to the speed difference to maintain aprescribed level of residuals within the cylinder.
 37. The method ofclaim 36, further comprising adjusting the amount of opening overlap inresponse to a rotational speed of the engine.
 38. The method of claim37, wherein the adjusting of overlap includes increasing the amount ofopening overlap as the rotational speed of the engine increases relativeto the rotational speed of the compressor.
 39. The method of claim 36,further comprising adjusting the amount of opening overlap in responseto a rotational speed of the turbine.
 40. The method of claim 39,wherein the adjusting of overlap includes increasing the amount ofopening overlap as the rotational speed of the turbine increasesrelative to the rotational speed of the compressor.
 41. The method ofclaim 36, wherein the compressor is rotationally uncoupled from anyturbine and the turbine is rotationally uncoupled from any intakecompressor; and wherein the compressor and the turbine rotate aboutdifferent axes.
 42. The method of claim 36, wherein a first electricmachine drives the compressor, and the turbine drives a second electricmachine rotationally un-coupled with the first electric machine, whereinthe compressor operates at the different speed than the turbine byadjusting an amount of electrical energy provided to the compressor tovary the speed of the first electric machine relative to the speed ofthe second electric machine.
 43. A method for an engine cylinder with anintake and exhaust valve, comprising: operating an electrically-drivenintake compressor at a different speed than an exhaust-driven turbinecoupled to an electric machine; adjusting the compressor to reduce surgewhile continuing turbine operation; adjusting the electric machine inresponse to exhaust over-temperature; and while adjusting thecompressor, adjusting an amount of opening overlap between the intakeand exhaust valves in response to the speed difference.